US6328314B1 - Cylinder head gasket - Google Patents

Cylinder head gasket Download PDF

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Publication number
US6328314B1
US6328314B1 US09/374,867 US37486799A US6328314B1 US 6328314 B1 US6328314 B1 US 6328314B1 US 37486799 A US37486799 A US 37486799A US 6328314 B1 US6328314 B1 US 6328314B1
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US
United States
Prior art keywords
cylinder head
gasket
cylinder
combustion chamber
cylinder block
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US09/374,867
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English (en)
Inventor
Osamu Jinno
Eisaburo Goto
Seiji Omura
Tatsuya Kawakita
Hideo Nakamura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Taiho Kogyo Co Ltd
Toyota Motor Corp
Original Assignee
Taiho Kogyo Co Ltd
Toyota Motor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Taiho Kogyo Co Ltd, Toyota Motor Corp filed Critical Taiho Kogyo Co Ltd
Assigned to TOYOTA JIDOSHA KABUSHIKI KAISHA, TAIHO KOGYO CO., LTD. reassignment TOYOTA JIDOSHA KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GOTO, EISABURO, JINNO, OSAMU, KAWAKITA, TATSUYA, NAKAMURA, HIDEO, OMURA, SEIJI
Priority to US09/963,309 priority Critical patent/US6705618B2/en
Application granted granted Critical
Publication of US6328314B1 publication Critical patent/US6328314B1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0818—Flat gaskets
    • F16J15/0825—Flat gaskets laminated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0818—Flat gaskets
    • F16J2015/085—Flat gaskets without fold over
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0818—Flat gaskets
    • F16J2015/0856—Flat gaskets with a non-metallic coating or strip
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0818—Flat gaskets
    • F16J2015/0875—Flat gaskets comprising welds

Definitions

  • the present invention relates to a cylinder head gasket used in an engine.
  • a cylinder head gasket is known in the art which comprises a first and a second gasket plate disposed in overlapping relationship, held sandwiched between a cylinder head and a cylinder block and each having a combustion chamber opening formed therein in alignment with a cylinder bore.
  • a gas in a combustion chamber may blow through a clearance between the cylinder head gasket and the cylinder head, between the cylinder head gasket and the cylinder block or between a first and a second gasket substrate which form together the cylinder head gasket.
  • a cylinder block which is made from aluminum has recently been employed, with a cast iron liner being usually provided on the cylinder bore in order to secure an abrasion resistance thereof.
  • a liner may be secured in place by a press fit or by a casting technique.
  • the end of the liner is formed with a flange, which is disposed in abutment against an offset step formed on the block, so that the both parts may be positioned and the liner can be secured by a press fit in the cylinder block.
  • a failure of a bead on the cylinder head gasket may occur in a region thereof which is contacted by a liner which projects above the surface of the cylinder block to cause an excessively high pressure of contact or the offset step on the cylinder block, which is abutted by the liner flange, may be deformed to cause a blow-through of a gas in the combustion chamber.
  • the likelihood of causing a blow-through of a gas in the combustion chamber also exists in a region of the cylinder head gasket which is contacted by a liner which remains depressed below the surface of the cylinder block to present an excessively low pressure of contact.
  • the surface pressure is high in a region located adjacent to one of the bolts while the surface pressure decreases with a distance from the bolts, causing a degradation in the sealing performance of some engines at a distance from the clamping bolts, again giving rise to the likelihood of producing a blow-through of a gas in the combustion chamber.
  • the present invention provides a cylinder head gasket capable of preventing the occurrence of a blow-through of a combustion gas more effectively.
  • the invention also provides a cylinder head gasket which allows the occurrence of a blow-through of a combustion gas to be prevented by enabling a surface pressure which is as even as possible to be achieved when a cylinder head and a cylinder block are clamped together by clamping bolts.
  • a cylinder head gasket including a first and a second gasket substrate disposed in overlapping relationship, held sandwiched between a cylinder head and a cylinder block and each having a combustion chamber opening formed therein in alignment with a cylinder bore, the first gasket substrate being disposed toward the cylinder head and formed with a first inner projection surrounding the combustion chamber opening and projecting toward the cylinder head and the second gasket substrate being disposed toward the cylinder block and formed with a second inner projection surrounding the combustion chamber opening and projecting toward the cylinder block, the first and the second gasket substrate being disposed in overlapping relationship to define a clearance between the first and the second inner projection which project in opposite direction from each other, the first and the second gasket substrate being held sandwiched between the cylinder head and the cylinder block in a manner to cause a plastic deformation of the first and the second inner projection toward the clearance defined therebetween.
  • a cylinder head gasket of a conventional type as mentioned above is characterized in that the first gasket substrate which is disposed toward the cylinder head is formed with a first inner projection surrounding the combustion chamber opening and projecting toward the cylinder head and including a radially central part which projects toward the cylinder block, that the second gasket substrate which is disposed toward the cylinder block is formed with a second inner projection surrounding the combustion chamber opening and projecting toward the cylinder block and including a radially central part which projects toward the cylinder head, and that the first and the second gasket substrate are disposed in overlapping relationship such that at least when they are assembled into an engine, the radially central part the first inner projection and the radially central part of the second inner projection are disposed to be in close contact with each other continuously in the circumferential direction.
  • the first inner projection of the first gasket substrate and the second inner projection of the second gasket substrate undergo a plastic deformation in a direction toward the clearance defined therebetween.
  • both inner projections will undergo a magnitude of a plastic deformation which varies in accordance with the surface pressure, with a consequence that there is secured an even pressure of contact, enabling a local blow-through to be prevented.
  • the radially central part of the first inner projection which projects toward the cylinder block and the radially central part of the second inner projection which projects toward the cylinder head are disposed to be in close contact with each other, continuously in the circumferential direction, and accordingly, the pressure of any combustion gas which tends to blow through a clearance therebetween urges the first inner projection toward the cylinder head and urges the second inner projection toward the cylinder block.
  • the sealing performance thereof is improved.
  • the sealing performance thereof is improved.
  • FIG. 1 is a plan view of a first embodiment of the invention
  • FIG. 2 is a cross section taken along the line II—II shown in FIG. 1;
  • FIG. 3 is a cross section taken along the line III—III shown in FIG. 1;
  • FIG. 4 is an enlarged cross section of part shown in FIG. 3;
  • FIG. 5 is an enlarged section illustrating a plastic deformation of an increased magnitude of a first inner projection 2 A and a second inner projection 3 A;
  • FIG. 6 is an enlarged cross section illustrating a plastic deformation of a reduced magnitude of the first inner projection 2 A and the second inner projection 3 A;
  • FIG. 7 is a cross section of a second embodiment of the invention.
  • FIG. 8 is a cross section of a third embodiment of the invention.
  • FIG. 9 is a cross section of a fourth embodiment of the invention.
  • FIG. 10 is a cross section of a fifth embodiment of the invention.
  • FIG. 11 is a cross section taken at a different position from FIG. 10 .
  • a cylinder head gasket 1 comprises a first gasket substrate 2 and a second gasket substrate 3 of a relatively increased thickness which are disposed in overlapping relationship.
  • a first plate 4 and a second plate 5 of a relatively reduced thickness are disposed in overlapping relationship with the front and the back surface of the assembly of gasket substrates.
  • four combustion chamber openings 10 are formed through the gasket substrates 2 , 3 and the plates 4 , 5 in alignment with a cylinder bore 9 of an engine as are bolt holes 11 for passing clamping bolts, not shown, and water holes 12 through which a cooling water is passed.
  • the gasket substrates 2 , 3 and the plates 4 , 5 are integrally fastened together by means such as lancelock.
  • the cylinder head gasket 1 is interposed between a cylinder head (not shown), and a cylinder block 13 of an engine, which are integrally fastened together by clamping bolts mentioned above, whereby the gasket 1 is held sandwiched therebetween to provide a seal therebetween.
  • the upper or the first gasket substrate 2 which is disposed toward a cylinder head, not shown, is formed with a first inner projection 2 A surrounding the combustion chamber opening 10 and projecting toward the cylinder head while the lower or the second gasket substrate 3 , which is disposed toward the cylinder block 13 , is formed with a second inner projection 3 A surrounding the combustion chamber opening 10 and projecting toward the cylinder block 13 .
  • the first and the second inner projection 2 A, 3 A are formed symmetrically to each other with respect to a mating surface between the substrates 2 , 3 , and when both gasket substrates 2 , 3 are disposed in an overlapping relationship, a clearance or an air gap 14 (see FIG. 4) is defined between the first and the second inner projections 2 A, 3 A which project in opposite directions.
  • first gasket substrate 3 is formed with a first outer projection 2 B surrounding the first inner projection 2 A and projecting toward the cylinder head
  • second gasket substrate 3 is formed with a second outer projection 3 B surrounding the second inner projection 3 A and projecting toward the cylinder block 13 .
  • the first and the second outer projection 2 B, 3 B are also formed symmetrically to each other with respect to a mating surface between the both gasket substrates 2 , 3 , whereby when the both gasket substrates 2 , 3 are disposed in overlapping relationship, a clearance or an air gap 15 (see FIG. 4) can be defined between the first and the second outer projection 2 B, 3 B which project in opposite directions.
  • first and the second inner projection 2 A, 3 A are formed as annular grooves which surround the combustion chamber opening 10 and which define the air gap 14 .
  • each of these annular grooves is formed with a sidewall 2 Aa, or 3 Aa which is located on the inner periphery or toward the combustion chamber opening 10 and another sidewall 2 Ab or 3 Ab on the outer periphery.
  • the opposing surfaces of the first and the second outer projection 2 B, 3 B are not formed as annular grooves but are formed as recesses.
  • the both outer projections 2 B, 3 B are formed with sidewalls 2 Ba, 3 Ba toward the combustion chamber opening 10 so as to surround it, but are not provided with sidewalls on the other side.
  • the air gap 15 will be formed between the sidewalls 2 Ba, 3 Ba which are adjacent to each other, as shown in FIG. 3, but the inner surfaces of the both outer projections 2 B, 3 B which are formed as recesses will contact each other in regions other than the region between the pair of adjacent combustion chamber openings 10 .
  • the air gap 15 is formed in an extent lying between the sidewalls 2 Ba, 3 Ba to an area of contact between the both recessed surfaces.
  • the first plate 4 is formed with a first full bead 4 A which surrounds the combustion chamber opening 10 and a first half bead 4 B which surrounds the first full bead 4 A, the first full bead 4 A being formed to project toward the first inner projection 2 A of the first gasket substrate 2 and the first half bead 4 B being formed to project toward the first outer projection 2 B of the first gasket substrate 2 .
  • the second plate 5 is formed with a second full bead 5 A which surrounds the combustion chamber opening 10 and a second half bead 5 B which surrounds the second full bead 5 A, the second full bead 5 A being formed to project toward the second inner projection 3 A of the second gasket substrate 3 and the second half bead 5 B being formed to project toward the second outer projection 3 B of the second gasket substrate 3 .
  • the full beads 4 A, 5 A and the half beads 4 B, 5 B are formed to define a surface symmetry.
  • the cylinder block 13 is provided with a liner 16 , as shown in FIGS. 2 and 3, and the liner 16 is formed with a flange 16 A at its top end which extends radially outward.
  • the liner 16 is secured as a press fit in the cylinder block 13 , and the bottom surface of the flange 16 A is disposed in abutment against the upper surface of an offset step 13 A formed in the cylinder block 13 , thereby positioning the liner 16 on the cylinder block 13 .
  • the first inner projection 2 A of the first gasket substrate 2 , the second inner projection 3 A of the second gasket substrate 3 , the first full bead 4 A of the first plate 4 and the second full bead 5 A of the second plate 5 are placed as an overlapping assembly on top of the flange 16 A of the liner 16 .
  • first outer projection 2 B of the first gasket substrate 3 the second outer projection 3 B of the second gasket substrate 3 , the first half bead 4 B of the first plate 4 and the second half bead 5 B of the second plate 5 are placed, as an overlapping assembly, on top of the cylinder block 13 on the outer side of the flange 16 A.
  • the cylinder head gasket 1 is held between the cylinder head and the cylinder block 13 by the clamping bolts mentioned above.
  • the cylinder head gasket 1 is interposed between the cylinder head and the cylinder block 13 of an engine, and is sealed therebetween by integrally fastening the cylinder head and the cylinder block 13 by clamping bolts.
  • the first inner projection 2 A of the first gasket plate 2 and the second inner projection 3 A of the second gasket plate 3 undergo a plastic deformation toward the air gap 14 under the influence of the surface pressure, and the first outer projection 2 B of the first gasket substrate 2 and the second outer projection 3 B of the second gasket substrate 3 also undergo a plastic deformation toward the air gap 15 .
  • the surface pressure will be high at a position adjacent to the bolt hole 11 , but will be low at a position which is removed from the bolt hole 11 .
  • the first inner projection 2 A and the second inner projection 3 A experience a magnitude of a plastic deformation in the circumferential direction of the combustion chamber opening 10 which varies depending on the magnitude of the surface pressure, whereby it is possible to maintain as even a surface pressure as possible in the circumferential direction of the combustion chamber opening 10 .
  • the first inner projection 2 A and the second inner projection 3 A will experience an increased magnitude of plastic deformation toward the air gap 14 under the influence of the surface pressure, as illustrated in FIG. 5, but it will be noted that regions close to the sidewalls 2 Aa, 2 Ab, 3 Aa and 3 Ab of the respective projections 2 A, 3 A are less susceptible to plastic deformation than the central regions, whereby these sidewall regions act as bead stops, thus preventing the respective full beads 4 A, 5 A from being excessively compressed and damaged.
  • the first outer projection 2 B, the second outer projection 3 B, the first half bead 4 B and the second half bead 5 B are less susceptible to plastic deformation than the central regions, whereby these sidewall regions act as bead stops, thus preventing the respective full beads 4 A, 5 A from being excessively compressed and damaged.
  • FIG. 7 shows a second embodiment of the invention in which the inner projections 2 A, 3 A are left free without placing them in close contact toward the combustion chamber opening 10 while the outer projections 2 B, 3 B are formed with sidewalls on both the inner and the outer periphery so that the outer projections are disposed in close contact with each other on the outside of the both sidewalls.
  • the full beads 4 A, 5 A and the half beads 4 B, 5 B are interchanged in position as compared with the first embodiment, with the half beads 4 B, 5 B being disposed in overlapping relationship with the corresponding inner projections 2 A, 3 A and the full beads 4 A, 5 A being disposed in overlapping relationship with the outer projections 2 B, 3 B.
  • the full beads 4 A, 5 A and the outer projections 2 B, 3 B are disposed nearer the combustion chamber opening 10 than in the first embodiment, whereby the inner periphery of the outer projections 2 B, 3 B is disposed in overlapping relationship with the liner 16 and the full beads 4 A, 5 A are disposed across the liner 16 and the cylinder block 13 .
  • FIG. 8 shows a third embodiment of the invention in which the first outer projection 2 B of the first gasket substrate 3 , the second outer projection 3 B of the second gasket substrate 3 , the first half bead 4 B of the first plate 4 and second half bead 5 B of the second plate 5 shown in the first embodiment are omitted.
  • a shim 21 is disposed within the air gap 14 in order to improve the sealing performance. It is preferred that the shim 21 be secured to at least one of the gasket substrates 2 and 3 for handling reasons, and may be secured to the second gasket substrate 3 by spot welding along the center line of the shim 21 .
  • the shim 21 has a thickness which is preferably equal to or less than one-half the height of the air gap 14 defined between the inner projections 2 A and 3 A.
  • a resin layer may be provided by a resin sheet which is adhesively bonded or by providing a resin coating.
  • the resin layer comprises polyamide or polyamideimide which exhibits high heat resistance, and which may be blended with a filler such as a graphite, carbon fiber, glass fiber or clay in order to improve the strength, the heat resistance and/or adhesion.
  • a scarfed layer may be provided in place of the shim 21 or a resin layer. It should be understood that any one of shim 21 , a resin layer or a scarfed layer may also be provided in the first or second embodiment.
  • FIG. 9 shows a fourth embodiment of the invention, which is fundamentally constructed in the similar manner as the first embodiment.
  • the strengths of the inner projections 2 A, 3 A disposed toward the full beads 4 A, 5 A are chosen to be greater than the strengths of the outer projections 2 B, 3 B disposed toward the half beads 4 B, 5 B.
  • the amount of projection hf of each of the inner projections 2 A, 3 A is chosen to be larger than the amount of projection hh of the outer projections 2 B, 3 B.
  • an angle of rise ⁇ f of each sidewall of the inner projections 2 A, 3 A may be chosen to be greater than an angle of rise ⁇ h of each sidewall of the outer projections 2 B, 3 B.
  • the strengths of the inner projections 2 A, 3 A disposed toward the full beads 4 A, 5 A are chosen to be greater than the strengths of the outer projections 2 B, 3 B disposed toward the half beads 4 B, 5 B, the surface pressure which is generated in the region of the full beads 4 A, 5 A during the clamping operation becomes greater than the surface pressure generated in the region of the half beads 4 B, 5 B, thus providing a more optimized sealing performance.
  • a sealing force which is generally required for a half bead is on the order of 0.3 to 0.4 MPa, which is necessary in order to prevent an ingress of cooling water onto the end face of the liner and to prevent a gas which may leak from the full bead from becoming mixed into the cooling water.
  • a sealing force which is required for a full bead is on the order of 6 to 9 MPa, which is necessary to seal against the explosion pressure of an engine. According to the type of the engine, a higher sealing force for a full bead will be required. Thus, the sealing force required of the full bead is greater than the sealing force required of the half bead.
  • a clearance between the cylinder head and the cylinder block is designed to be narrow in a peripheral region and wider in a region adjacent to the bore. Accordingly, if the inner projections 2 A, 3 A has an offset height which is chosen to be the same as that the outer projections 2 B, 3 B, the surface pressure in the region of the outer projections 2 B, 3 B will be relatively higher, which is undesirable.
  • the sealing force of the outer projections 2 B, 3 B may be chosen such that the half beads are capable of sealing the cooling water when the liner 16 projects above the surface of the cylinder block 13 .
  • first inner projection 2 A and the second inner projection 3 A have an identical cross section circumferentially of the combustion chamber opening 10 , but their shapes may be changed depending on the location of the bolt holes 11 associated with clamping bolts so that a more even surface pressure prevails adjacent to and removed from the bolt holes 11 .
  • the amount of projection h of each of the inner projections 2 A, 3 A, as illustrated in FIG. 4 may be reduced, its radial width w increased or an angle of rise ⁇ of each sidewall reduced in comparison to a corresponding quantity at a position removed from the bolt hole 11 .
  • these choices may be used in combination.
  • a design may be employed which provides a slightly higher surface pressure in the region adjacent to the combustion chamber opening 10 .
  • FIG. 10 shows a fifth embodiment of the invention, which is fundamentally constructed in the similar manner as the first embodiment.
  • an upper or a first gasket substrate 102 which is disposed toward a cylinder head, not shown, is formed with a first inner projection 102 A surrounding a combustion chamber opening 110 and projecting toward the cylinder head and including a radially central part 102 a projecting downward or toward a cylinder block, not shown, presenting an arcuate configuration in section.
  • a lower or a second gasket substrate 103 disposed toward the cylinder block is formed with a second inner projection 103 A surrounding the combustion chamber opening 110 and projecting downward and including a radially central part 103 a which is arcuate in section and projecting upward or toward the cylinder block.
  • the first inner projection 102 A and the second inner projection 103 A are formed symmetrically to each other with respect to a mating surface between the both gasket substrates 102 , 103 , and when the both gasket substrates 102 , 103 , are disposed in overlapping relationship, the radially central part 102 a of the first inner projection 102 A and the radially central part 103 a of the second inner projection 103 A are disposed to be in close contact with each other continuously in the circumferential direction.
  • the first gasket substrate 103 is also formed with a first outer projection 102 B surrounding the first inner projection 102 A and projecting upward, and the second gasket substrate 103 is formed with a second outer projection 103 B surrounding the second inner projection 103 A and projecting downward.
  • the first outer projection 102 B and the second outer projection 103 B are also formed symmetrically to each other with respect to a mating surface between the both gasket substrates 102 , 103 , and when both gasket substrates 102 , 103 are disposed in overlapping relationship, the first outer projection 102 B and the second outer projection 103 B which project in opposite directions are spaced from each other on their side located adjacent to the combustion chamber opening 110 , but are disposed to be in close contact with each other at a position which is by a given distance removed on the opposite side or away from the combustion chamber opening 110 .
  • first inner projection 102 A and the second inner projection 103 A have a height and an angle of rise along its inner and outer peripheries which vary in the circumferential direction.
  • FIG. 10 shows a cross section at an intermediate position between bolt holes through which the clamping bolts are passed (see the location indicated by the line III—III shown in FIG. 1 ), and it will be seen that at this position, the first inner projection 102 A and the second inner projection 103 A have an increased height h 1 along the inner and outer peripheries and have an increased angle of rise ⁇ 1 from the body of the gasket substrates 102 , 103 .
  • FIG. 10 shows a cross section at an intermediate position between bolt holes through which the clamping bolts are passed (see the location indicated by the line III—III shown in FIG. 1 ), and it will be seen that at this position, the first inner projection 102 A and the second inner projection 103 A have an increased height h 1 along the inner and outer peripheries and have an increased angle of rise ⁇ 1 from the body of the gas
  • FIG. 11 shows a corresponding cross section taken at a position which is close to a bolt hole through which a clamping bolt is passed.
  • the first projection 102 A and the second inner projection 103 A have a reduced height h 2 and a reduced angle of rise ⁇ 2 along the inner and outer peripheries.
  • the heights h 1 , h 2 and angles ⁇ 1 , ⁇ 2 prevail over a given extent centered about the intermediate position between the bolt holes and the position close to the bolt holes, with both the height and the angle smoothly changing from one of the values to the other.
  • a first plate 104 is formed with a first full bead 104 A which surrounds the combustion chamber opening 110 and a first half bead 104 B which surrounds the first full bead 104 A, the first full bead 104 A being formed to project toward the first inner projection 102 A of the first gasket substrate 102 and the first half bead 104 B being formed to project toward the first outer projection 102 B of the first gasket substrate 102 .
  • a second plate 105 is formed with a second full bead 105 A which surrounds the combustion chamber opening 110 and a second half bead 105 B which surrounds the second full bead 105 A, the second full bead 105 A being formed to project toward the second inner projection 103 A of the second gasket substrate 103 and the second half bead 105 B being formed to project toward the second outer projection 103 B of the second gasket substrate 103 .
  • these full beads 104 A, 105 A and the half beads 104 B, 105 B are formed to provide a surface symmetry.
  • the cylinder head gasket 101 is interposed between a cylinder head and a cylinder block of an engine, and is sealed therebetween by integrally fastening the cylinder head and the cylinder block by using clamping bolts.
  • the surface pressure at a position close to the clamping bolt is increased and is reduced at a position removed therefrom.
  • the first inner projection 102 A and the second inner projection 103 A have a circumferentially varying height, as indicated at h 1 and h 2 , and also a circumferentially varying angle of rise, as indicated at ⁇ 1 , ⁇ 2 , along the inner and outer peripheries thereof, the surface pressure applied to the first inner projection 102 A and the second inner projection 103 A can be made as even as possible when viewed in the circumferential direction of the combustion chamber opening 110 .
  • any combustion gas which tends to blow through a clearance between the first inner projection 102 A and the second inner projection 103 A to the exterior exhibits a pressure which urges the first inner projection 102 A toward the cylinder head and which simultaneously urges the second inner projection 103 A toward the cylinder block.
  • the surface pressure acting between the first inner projection and the cylinder head then increases, thus improving the sealing performance of such region.
  • the surface pressure acting between the second inner projection and the cylinder block increases, also improving the sealing performance in such region.
  • first gasket substrate 102 and the second gasket substrate 103 are pressed against each other at the same time as they are pressed against the cylinder head and the cylinder block, respectively, under the pressure of the combustion gas, thus preventing a blow-through of the combustion gas more effectively than in the prior art.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gasket Seals (AREA)
US09/374,867 1998-09-18 1999-08-16 Cylinder head gasket Expired - Fee Related US6328314B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US09/963,309 US6705618B2 (en) 1998-09-18 2001-09-26 Cylinder head gasket

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JP26426398A JP4032270B2 (ja) 1998-09-18 1998-09-18 シリンダヘッドガスケット
JP10-264263 1998-09-18

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US09/963,309 Expired - Fee Related US6705618B2 (en) 1998-09-18 2001-09-26 Cylinder head gasket

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EP (2) EP0987474B1 (de)
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Cited By (26)

* Cited by examiner, † Cited by third party
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US6478302B1 (en) * 1999-12-27 2002-11-12 Ishikawa Gasket Co., Ltd. Metal laminate gasket with identification sign
US20030042689A1 (en) * 2001-09-05 2003-03-06 Armin Diez Cylinder head gasket
US6575473B2 (en) * 2000-09-04 2003-06-10 Nippon Gasket Co., Ltd. Metallic gasket
US20030151210A1 (en) * 2001-03-07 2003-08-14 Kosaku Ueta Metal gasket
US6644669B2 (en) * 2000-03-29 2003-11-11 Dana Corporation Flat metal gasket
US20040012154A1 (en) * 2000-10-12 2004-01-22 Gunther Unseld Multi-layered steel gasket
US6705618B2 (en) * 1998-09-18 2004-03-16 Taiho Kogyo Co., Ltd. Cylinder head gasket
US6712364B2 (en) * 2000-12-12 2004-03-30 Dana Corporation Cylinder head gasket
US20040217552A1 (en) * 2003-03-26 2004-11-04 Masakazu Sueda Metal gasket
US20050046117A1 (en) * 2003-08-28 2005-03-03 Martin Novil Sealing gasket with flexible stopper
US20050046120A1 (en) * 2003-08-28 2005-03-03 Martin Novil Sealing gasket with flexible stopper
US20050151327A1 (en) * 2004-01-09 2005-07-14 Ishikawa Gasket Co., Ltd. Cylinder head gasket
US20060197288A1 (en) * 2005-03-03 2006-09-07 Ishikawa Gasket Co., Ltd. Metal laminate cylinder head gasket
US20070200301A1 (en) * 2003-08-28 2007-08-30 Freudenberg-Nok General Partnership Sealing Gasket With Flexible Stopper
US20080246232A1 (en) * 2007-01-16 2008-10-09 Uchiyama Manufacturing Corp. Gasket
US20090033039A1 (en) * 2005-06-28 2009-02-05 Freudenberg-Nok General Partnership Gasket with asymmetric bead arrangement
US20110049813A1 (en) * 2009-09-03 2011-03-03 Hyundai Motor Company Gasket for exhaust pipe of vehicle
US20110095489A1 (en) * 2009-10-22 2011-04-28 Paul Fatora Gasket with engine liner accomodation
US20110133414A1 (en) * 2009-12-03 2011-06-09 Hyundai Motor Company Gasket unit
US20120175847A1 (en) * 2011-01-12 2012-07-12 Popielas Frank W Support wave stopper in web area of multi-layered steel cylinder head gasket
US20140042705A1 (en) * 2012-08-10 2014-02-13 Dana Automotive Systems Group, Llc Multi-layered gasket
US20140042711A1 (en) * 2012-08-10 2014-02-13 Dana Automotive Systems Group, Llc Metal gasket with coating topography
US20150204270A1 (en) * 2014-01-17 2015-07-23 Federal-Mogul Corporation Gasket component with half-stop and method of manufacturing
US20160334016A1 (en) * 2014-01-28 2016-11-17 Elringklinger Ag Cylinder-head gasket, and a sealing system comprising such a gasket
US20180266559A1 (en) * 2015-11-25 2018-09-20 Elringklinger Ag Flat gasket and sealing assembly containing a flat gasket
US20220243815A1 (en) * 2021-02-02 2022-08-04 Tenneco Inc. Combustion cylinder head gasket

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7000924B2 (en) * 2000-06-15 2006-02-21 Dana Corporation Flat gasket and method for the production thereof
DE10218245A1 (de) 2002-04-24 2003-11-13 Elringklinger Ag Zylinderkopfdichtung
JP3908745B2 (ja) * 2004-03-09 2007-04-25 石川ガスケット株式会社 金属積層形ガスケット
CA2577172A1 (en) * 2004-07-16 2006-02-23 Dana Corporation Fluid aperture with stopper bead
DE102004044851A1 (de) * 2004-09-10 2006-03-16 Elringklinger Ag Zylinderkopfdichtung
DE102004056638A1 (de) * 2004-11-24 2006-10-12 Federal-Mogul Sealing Systems Gmbh Flachdichtung
DE102005019689A1 (de) * 2005-04-28 2006-11-16 Elringklinger Ag Flachdichtung, insbesondere Zylinderkopfdichtung
DE102005020923A1 (de) * 2005-05-04 2006-11-16 Federal-Mogul Sealing Systems Gmbh Flachdichtung, insbesondere Zylinderkopfdichtung
JP4534097B2 (ja) 2007-09-12 2010-09-01 日本ガスケット株式会社 シリンダヘッドガスケット
US8632077B2 (en) 2008-02-13 2014-01-21 Federal-Mogul Corporation Multilayer static gasket with bead compression limiter
DE102008020277B4 (de) * 2008-04-23 2016-06-30 Elringklinger Ag Zylinderkopfdichtung
US20110127729A1 (en) * 2008-09-18 2011-06-02 Yasumaro Takeda Cylinder head gasket

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3835524A (en) * 1973-08-13 1974-09-17 Massey Welding Co Method of manufacturing rejuvenated scarfing blocks
US4428593A (en) * 1981-07-10 1984-01-31 Felt Products Mfg. Co. Gasket assembly having improved sealing characteristics and method of making same
US4721315A (en) * 1985-12-27 1988-01-26 Nihon Metal Gasket Kabushiki Kaisha Metallic cylinder head gasket
US5205566A (en) * 1989-04-14 1993-04-27 Nihon Metal Gasket Kabushiki Kaisha Metallic gasket
US5230521A (en) * 1991-01-11 1993-07-27 Nihon Metal Gasket Co., Ltd. Metallic laminate gasket with plates of different bead widths fixed together
US5232229A (en) * 1990-08-07 1993-08-03 Ishikawa Gasket Co., Ltd. Metal gasket with low heat transmission
JPH08100859A (ja) 1994-08-05 1996-04-16 Nippon Gasket Co Ltd 金属製ガスケット
JPH08114266A (ja) 1994-10-17 1996-05-07 Ket & Ket:Kk 金属ガスケット
US5601292A (en) * 1994-03-14 1997-02-11 Nippon Leakless Industry Co., Ltd. Metal gasket assembly with shims
US5863046A (en) * 1996-02-17 1999-01-26 Elring Klinger Gmbh Cylinder head gasket with deformable deformation limiter
US5876038A (en) * 1995-04-26 1999-03-02 Elring Klinger Gmbh Metallic cylinder head gasket
US6145847A (en) * 1997-01-13 2000-11-14 Nippon Reinz Co., Ltd. Metal laminate gasket

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2523321B2 (ja) 1987-05-27 1996-08-07 日本メタルガスケット株式会社 積層金属ガスケット
JP2610891B2 (ja) 1987-09-11 1997-05-14 日本メタルガスケット株式会社 積層金属ガスケット
JPH0261171A (ja) 1988-06-10 1990-03-01 Mitsuo Fujisawa 布素材に於ける縁飾り切口の構造とその加工装置
JPH01118149A (ja) 1988-09-30 1989-05-10 Ricoh Co Ltd 画像記録方法
JPH0536135Y2 (de) * 1990-02-01 1993-09-13
JP3054457B2 (ja) 1991-04-03 2000-06-19 大豊工業株式会社 金属ガスケット
JP3126418B2 (ja) 1991-07-08 2001-01-22 トヨタ自動車株式会社 金属ガスケット
JP3083375B2 (ja) * 1991-10-15 2000-09-04 日本ガスケット株式会社 エキゾーストマニホルドガスケット等のガスケット
JP3118043B2 (ja) 1991-10-24 2000-12-18 大豊工業株式会社 金属ガスケット
DE4238669C2 (de) * 1992-11-17 1999-02-11 Kempchen & Co Gmbh Absperrarmatur
JP3197395B2 (ja) * 1993-01-14 2001-08-13 日本メタルガスケット株式会社 金属ガスケット
JPH07253162A (ja) * 1994-06-30 1995-10-03 Nippon Riikuresu Kogyo Kk メタルガスケット
DE69634031D1 (de) * 1995-11-07 2005-01-20 Nicholsons Aircraft Seals Ltd Abdichtung
US5979906A (en) * 1997-02-13 1999-11-09 Farnam/Meillor Sealing Systems Inc. Multi-layered metal gasket assembly and method of constructing the same
US5906376A (en) * 1997-04-24 1999-05-25 Ishikawa Gasket Co., Ltd. Metal gasket with locally heated-treating bead
DE19731489C2 (de) * 1997-07-22 2001-09-20 Reinz Dichtungs Gmbh Metallische Flachdichtung
JP4032270B2 (ja) * 1998-09-18 2008-01-16 大豊工業株式会社 シリンダヘッドガスケット

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3835524A (en) * 1973-08-13 1974-09-17 Massey Welding Co Method of manufacturing rejuvenated scarfing blocks
US4428593A (en) * 1981-07-10 1984-01-31 Felt Products Mfg. Co. Gasket assembly having improved sealing characteristics and method of making same
US4721315A (en) * 1985-12-27 1988-01-26 Nihon Metal Gasket Kabushiki Kaisha Metallic cylinder head gasket
US5205566A (en) * 1989-04-14 1993-04-27 Nihon Metal Gasket Kabushiki Kaisha Metallic gasket
US5232229A (en) * 1990-08-07 1993-08-03 Ishikawa Gasket Co., Ltd. Metal gasket with low heat transmission
US5230521A (en) * 1991-01-11 1993-07-27 Nihon Metal Gasket Co., Ltd. Metallic laminate gasket with plates of different bead widths fixed together
US5601292A (en) * 1994-03-14 1997-02-11 Nippon Leakless Industry Co., Ltd. Metal gasket assembly with shims
JPH08100859A (ja) 1994-08-05 1996-04-16 Nippon Gasket Co Ltd 金属製ガスケット
US5609345A (en) 1994-08-05 1997-03-11 Nippon Gasket Co., Ltd. Metal gasket with stepped intermediate plate
JPH08114266A (ja) 1994-10-17 1996-05-07 Ket & Ket:Kk 金属ガスケット
US5876038A (en) * 1995-04-26 1999-03-02 Elring Klinger Gmbh Metallic cylinder head gasket
US5863046A (en) * 1996-02-17 1999-01-26 Elring Klinger Gmbh Cylinder head gasket with deformable deformation limiter
US6145847A (en) * 1997-01-13 2000-11-14 Nippon Reinz Co., Ltd. Metal laminate gasket

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6705618B2 (en) * 1998-09-18 2004-03-16 Taiho Kogyo Co., Ltd. Cylinder head gasket
US6478302B1 (en) * 1999-12-27 2002-11-12 Ishikawa Gasket Co., Ltd. Metal laminate gasket with identification sign
US6644669B2 (en) * 2000-03-29 2003-11-11 Dana Corporation Flat metal gasket
US6575473B2 (en) * 2000-09-04 2003-06-10 Nippon Gasket Co., Ltd. Metallic gasket
US6923450B2 (en) * 2000-10-12 2005-08-02 Dana Corporation Multi-layered steel gasket
US20040012154A1 (en) * 2000-10-12 2004-01-22 Gunther Unseld Multi-layered steel gasket
US6712364B2 (en) * 2000-12-12 2004-03-30 Dana Corporation Cylinder head gasket
US20030151210A1 (en) * 2001-03-07 2003-08-14 Kosaku Ueta Metal gasket
US6827352B2 (en) * 2001-03-07 2004-12-07 Japan Metal Gasket Co., Ltd. Metal gasket
US20030042689A1 (en) * 2001-09-05 2003-03-06 Armin Diez Cylinder head gasket
US20040217552A1 (en) * 2003-03-26 2004-11-04 Masakazu Sueda Metal gasket
US7213813B2 (en) * 2003-03-26 2007-05-08 Ishikawa Gasket Co., Ltd. Metal gasket
US20070200301A1 (en) * 2003-08-28 2007-08-30 Freudenberg-Nok General Partnership Sealing Gasket With Flexible Stopper
US20050046120A1 (en) * 2003-08-28 2005-03-03 Martin Novil Sealing gasket with flexible stopper
US7234705B2 (en) * 2003-08-28 2007-06-26 Freudenberg-Nok General Partnership Sealing gasket with flexible stopper
US20050046117A1 (en) * 2003-08-28 2005-03-03 Martin Novil Sealing gasket with flexible stopper
US7137631B2 (en) * 2004-01-09 2006-11-21 Ishikawa Gasket Co., Ltd. Cylinder head gasket
US20050151327A1 (en) * 2004-01-09 2005-07-14 Ishikawa Gasket Co., Ltd. Cylinder head gasket
US20060197288A1 (en) * 2005-03-03 2006-09-07 Ishikawa Gasket Co., Ltd. Metal laminate cylinder head gasket
US20090033039A1 (en) * 2005-06-28 2009-02-05 Freudenberg-Nok General Partnership Gasket with asymmetric bead arrangement
US20080246232A1 (en) * 2007-01-16 2008-10-09 Uchiyama Manufacturing Corp. Gasket
US7832736B2 (en) * 2007-01-16 2010-11-16 Uchiyama Manufacturing Corp. Gasket
US20110049813A1 (en) * 2009-09-03 2011-03-03 Hyundai Motor Company Gasket for exhaust pipe of vehicle
US20110095489A1 (en) * 2009-10-22 2011-04-28 Paul Fatora Gasket with engine liner accomodation
US8336888B2 (en) * 2009-10-22 2012-12-25 Dana Automotive Systems Group, Llc Gasket with engine liner accomodation
US20110133414A1 (en) * 2009-12-03 2011-06-09 Hyundai Motor Company Gasket unit
US20120175847A1 (en) * 2011-01-12 2012-07-12 Popielas Frank W Support wave stopper in web area of multi-layered steel cylinder head gasket
US20140042705A1 (en) * 2012-08-10 2014-02-13 Dana Automotive Systems Group, Llc Multi-layered gasket
US20140042711A1 (en) * 2012-08-10 2014-02-13 Dana Automotive Systems Group, Llc Metal gasket with coating topography
US9394850B2 (en) * 2012-08-10 2016-07-19 Dana Automotive Systems Group, Llc Metal gasket with coating topography
US9476382B2 (en) * 2012-08-10 2016-10-25 Dana Automotive Systems Group, Llc Multi-layered gasket
US20150204270A1 (en) * 2014-01-17 2015-07-23 Federal-Mogul Corporation Gasket component with half-stop and method of manufacturing
US9863535B2 (en) * 2014-01-17 2018-01-09 Federal-Mogul Llc Gasket component with half-stop and method of manufacturing
US10443731B2 (en) * 2014-01-17 2019-10-15 Tenneco Inc. Gasket component with half-stop and method of manufacturing
US20160334016A1 (en) * 2014-01-28 2016-11-17 Elringklinger Ag Cylinder-head gasket, and a sealing system comprising such a gasket
US20180266559A1 (en) * 2015-11-25 2018-09-20 Elringklinger Ag Flat gasket and sealing assembly containing a flat gasket
US20220243815A1 (en) * 2021-02-02 2022-08-04 Tenneco Inc. Combustion cylinder head gasket

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EP0987474A3 (de) 2000-10-25
JP4032270B2 (ja) 2008-01-16
EP1398546B1 (de) 2005-08-03
EP1398546A1 (de) 2004-03-17
DE69921411T2 (de) 2005-10-20
US6705618B2 (en) 2004-03-16
DE69926552T2 (de) 2006-06-08
DE69921411D1 (de) 2004-12-02
US20020011709A1 (en) 2002-01-31
DE69926552D1 (de) 2005-09-08
EP0987474B1 (de) 2004-10-27
JP2000088105A (ja) 2000-03-31

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